US3860101A - Synchronous clutch assembly for a transmission device - Google Patents

Synchronous clutch assembly for a transmission device Download PDF

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Publication number
US3860101A
US3860101A US409919A US40991973A US3860101A US 3860101 A US3860101 A US 3860101A US 409919 A US409919 A US 409919A US 40991973 A US40991973 A US 40991973A US 3860101 A US3860101 A US 3860101A
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United States
Prior art keywords
splines
shuttle
input
input member
output member
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Expired - Lifetime
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US409919A
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English (en)
Inventor
Feo Angelo De
Edward F Drewniany
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Curtiss Wright Corp
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Curtiss Wright Corp
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Priority to US409919A priority Critical patent/US3860101A/en
Priority to NL7414014A priority patent/NL7414014A/nl
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
    • F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
    • F16H3/54—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears one of the central gears being internally toothed and the other externally toothed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/08—Serially-arranged clutches interconnecting two shafts only when all the clutches are engaged
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/02—Arrangements for synchronisation, also for power-operated clutches
    • F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
    • F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/78—Special adaptation of synchronisation mechanisms to these gearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/02—Arrangements for synchronisation, also for power-operated clutches
    • F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
    • F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
    • F16D2023/0618—Details of blocking mechanism comprising a helical spring loaded element, e.g. ball
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/02—Arrangements for synchronisation, also for power-operated clutches
    • F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
    • F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
    • F16D2023/0643—Synchro friction clutches with flat plates, discs or lamellae
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/02—Arrangements for synchronisation, also for power-operated clutches
    • F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
    • F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
    • F16D2023/0656—Details of the tooth structure; Arrangements of teeth

Definitions

  • the loading means alternately coacts with each of said input members for rotatively synchronizing the input member to be connected to the output member with the output member prior to drivable connection of the mechanism with the input member to be connected.
  • Another object of the present invention is to provide a synchronous clutch assembly for a transmission device which is capable of rotating an output member in opposite directions via two concentrically arranged rotatively driven input members and a single rectilinear motor means.
  • the present invention contemplates a novel synchronous clutch assembly for a transmission device, such as a planetary gear speed reducer, having dual, concentric, rotatively driven first and second input members, such as the ring gear and the planetary gear carrier of a planetary gear speed reducer, connected to be alternately driven in opposite directions by a prime mover, such as a gas turbine engine, and having an output member, such as a propeller, to be alternately rotated in such opposite directions.
  • the synchronous clutch assembly comprises a first spline means on said first and second input members and a switch means having second splines adapted to mesh with said first splines.
  • the switch means including a rectilinear, hydraulically actuated motor means, as for example a double-acting piston-cylinder mechanism, is supported for rotation and axial movement relative to the first and second input members.
  • the second spline means meshes with the first spline means of one of the first and second input members and in the other position meshes with the first spline means of the other first and second input members to effect rotation of the output member in the opposite direction.
  • the switching is preferably accomplished when the input members are rotatively disconnected from the prime mover by suitable-brake means,
  • a feature of this invention is the plurality of circumferentially spaced detents carried by the motor means and which coact with a clutch pack actuator or shuttle to engage a slip-clutch member and thereby impose a torque load or drag on the shuttle to cause the shuttle to rotate to a position to insure proper abutment of blocker splines prior to applying through the shuttle the full force on the slip-clutch member necessary to accelerate an input member to match that of the output member prior to moving the second spline means into mesh with the first spline means of the input member to be connected.
  • FIG. 1 is a schematic illustration of the synchronous clutch assembly according to this invention for a rotary transmission device
  • FIG. 2 is a fragmentary cross-sectional view of the synchronous clutch assembly shown schematically in FIG. 1;
  • FIG. 3 is an enlarged fragmentary view of the shuttle and slip clutches of the synchronous clutch assembly
  • FIG. 4 is a fragmentary view of the shuttle on a larger scale than shown in FIG. 3 and in one of its fully engaged torque transmitting positions;
  • FIG. 5 is a cross-sectional view taken substantially along line 5-5 of FIG. 4;
  • FIG. 6, 7, 8 and 9 are schematic views of the synchronous clutch assembly showing successive steps for switching from one torque transmitting position to the other.
  • reference number 10 generally designates the synchronous clutch assembly according to this invention shown as part of a rotation transmission device 12 having a planetary gear speed reducer 14 and a brake assembly 16. While synchronous clutch assembly 10 is shown and will be described as coacting with a planetary gear speed reducer and brake assembly, such as of the type disclosed in the aforesaid pending U.S. patent application Ser. No. 402,295 filed Oct. 1, 1973, the invention is not limited to such combination, but has application to any transmission device having dual, concentric input members driven by a prime mover.
  • the planetary gear speed reducer 14 comprises a sun gear 18, and a plurality of circumferentially spaced.
  • the planetary gears 20 disposed in mesh with the sun gear and an internal ring gear-22.
  • the planetary gears are supported for rotation by posts 23 mounted on a carrier 24.
  • the carrier is supported for rotation in a housing or casing 25.
  • the carrier 24 may have a tubular extension 26 which is supported at one end on an input or drive shaft 28, through bearings 30, while the opposite end is rotatively supported on bearings 31 on a pedestal 32 (schematically represented as a transverse wall in FIG. 1).
  • the drive shaft 28 is connected to a prime mover (not shown), such as a gas turbine engine (not shown), to effect rotation of sun gear 18.
  • the carrier 24 and ring gear 22 have connecting elements 34 and 36, respectively, which are alternately rotated by sun gear 18, depending upon whether the carrier or the ring gear is held against rotation by the brake assembly 16.
  • the connecting elements 34 and 36 will hereinafter be referred to'as a first input member and a second input member, respectively, which, as shown both in FIGS. 1 and 2 are concentrically supported relative to each other.
  • the brake assembly 16 comprises two annular brake subassemblies 38 and 40 which are operable through actuating means (not shown) to alternately arrest rotation of ring gear 20 or carrier 24, respectively.
  • This altcrnate braking of the ring gear and the carrier provides for opposite rotation of first and second input members 34 and 36.
  • an output member 42 which may be a shaft connected to drive a propeller (not shown)
  • synchronous clutch assembly 10 is disposed within casing 25 and connected to first and second input members 34 and 36.
  • the second input member 36 has an axial extension which is radially offset from the first input member 34 so as to provide an end portion 43 which is axially spaced from the end portion 45 of first input member 34, a portion of the assembly lying between end portions 43 and 45.
  • the synchronous clutch assembly 10 as shown in detail in FIGS. 2 to .5, comprises a switch means, including a double-acting piston-cylinder mechanism 44, and a torque loading means, including a shuttle 46 and a slip-clutch means 48.
  • the assembly 10 is supported for rotation within casing 25 by a fixed support structure 50 and two conventional oil transfer sleeves or no-load bearings 52 and 54 which function to effect transfer of oil from the stationary support structure 50 and rotating parts of assembly 10.
  • the double-acting piston-cylinder mechanism 44 has a piston consisting of an elongated cylindrical body portion 56 and an annular radially extending head portion 58 which serves to provide pressure surfaces.
  • the piston is supported for reciprocation relative to a cylinder structure which has two axially spaced, annular walls 60 and an axial extension 62.
  • the annular walls 60 and extension 62 define therebetween a working chamber 64 within which head portion 58 reciprocates.
  • the axial extension 62 is supported for rotation in noload bearing 54 and is spline connected at 66 to output shaft or member 42 for conjoined rotation with the latter.
  • Suitable seals 68 are provided between annular flanged portions 70 of walls 60.
  • suitable passageways 72 and 74 are provided to conduct pressurized fluid, such as oil, through no-load bearing 54 to and from working chamber 64 whereby head portion 58 is reciprocated in working chamber 64.
  • pressurized fluid such as oil
  • passageways 72 and 74 serve both as pressurized fluid supply conduits and return conduits, the supply conduit becoming a return conduit when pressurized fluid is introduced into the working chamber on the opposite side of piston head 58.
  • the piston includes a drive coupling or switch element 76 keyed at 78 to body portion 56.
  • the switch element 76 has an annular radially extending portion and a distal end portion 80 which extends axially between portions 45 and 43 of first and second input members 34 and 36.
  • the switch element 76 is spline connected at 82 to extension 62 of the cylinder structure so that switch element 76 is rotatable with extension 62 and output member 42 and is axially reciprocable relative to the extension and output member when the piston is reciprocated.
  • the switch element 76 is provided with axially spaced external splines 84 and 86 which are adapted alternately to engage internal splines 88 and 90 which are provided on the respective end portions 43 and 45.
  • the output member 42 is always in drivable connection with either the first or the second input member, there being no neutral position.
  • the switch element 76 also has a set of blocker splines 92 which are externally arranged on the periphery of an annular, radial extension 94 projecting between splines 88 and 90. Also carried by switch element 76 in extension 94 are a plurality of circumferentially spaced detent assemblies 96 which coact with shuttle 46 to engage clutch means 48 as will be more fully explained hereinafter.
  • the shuttle 46 is an annular member comprising two portions 98 and 100 bolted together at 102 and supported for axial movement, through clutch packs 104 and 106 of slip clutch means 48, on end portions 45 and 43 of first and second input members 34 and 36.
  • the shuttle 46 has two sets of axially spaced internal blocker splines 108 and 110 which coact with external blocker splines 92 of switch element 76 of mechanism 44 to properly align splines 84 and 86 with splines 88 and 90 prior to their movement into meshing relationship as will be more fully discussed herein.
  • shuttle 46 has internal splines 112 which are adapted to mesh with splines 86 of switch element 76and are axially so positioned relative to blocker splines 92, 108 and 110 that when the blocker splines are not in rotative engagement during a phase of reciprocative movement of switch element 76 splines [12 can be brought into mesh with splines 86 to thereby maintain the rotative interconnection of shuttle 48 with switch element 76.
  • the clutch pack 104 which may be referred to as the forward clutch pack, comprises a plurality of interjacent ringshaped discs 114 which are alternately spline connected to shuttle portion 100 and end portion 43 of second input member 36.
  • clutch pack 106 which may be referred to as the reverse clutch pack.
  • first or the second input member is brought into substantial rotative coincidence with the output member 42.
  • each of the detents 96 comprises a cylinder 118 which is slidably disposed in a bore 120 in extension 94 of end portion 80 of switch element 76.
  • a spring 122 is disposed in bore 120 to bias cylinder 118 radially outward toward shuttle 48.
  • the cylinder 118 has a teat-like portion 124 which is sized to fit within an annular camming groove 126 formed in shuttle 48.
  • each of the detents 96 The function of each of the detents 96 is to apply, upon reciprocativ'e movement of switch element 76, a torque load or drag onshuttle 48. This torque force is achieved by reason of the engagement of teat-like portion 124 of each of the detents on the shuttle, the torque load diminishing as teat-like portions 124 ride down the inclined side walls 128 of camming groove 126 and increases again as it rides upwardly on the opposite inclined side wall 128.
  • the springs 122 of each detent 96 resists the radial inward movement of cylinder 118.
  • the detents 96 also function to provide an axial force on shuttle 48 when the teat-like portions 124 ride upwardly on the inclined surface 128 of groove 126.
  • blocker splines 108 are circumferentially offset from blocker splines 110 so that upon axial movement of blocker splines 92, blocker splines 108 or 110 are in the line of travel of blocker splines 92.
  • each of the blocker splines 92 have two inclined surfaces 130 and 132 at their opposite ends. These surfaces 130 and 132 are complementary to similar inclined or chamfered end portions 134 and 136 of splines 108 and 110.
  • splines 112 and 86 are in number half of the number of splines 88 and 90 on the end portions 43 and 45 of first and second input members 34 and 36.
  • limited relative rotative movement between switch element 76 and shuttle 48 is permitted in both directions of travel of the shuttle by reason of the excess spacing between splines 112 and 86 (see FIG. 5).
  • This tangential movement limited by the abutment of splines 112 and 86 as shown in FIG. 8 provides for automatically positioning splines 86 with respect to splines in proper meshing alignment prior tosuch meshing.
  • the tangential movement limited by the abutment of splines 112 and 86 along their opposite sides provides for automatically aligning splines 84 for meshing with splines 88.
  • mechanism 44 may be provided with a locking device 140 which functions to hold the piston and hence drive coupling or switch element 76 in one of its two positions.
  • the device 140 serves to hold the piston and switch element 76 in the forward mode of operation (splines 80 and 88 in mesh) which, at sea, is sustained for days or weeks at a time.
  • pressurized fluid for those long periods need not'be constantly supplied to working chamber 64 to hold the piston in the selected position.
  • the locking device 140 may be a pin 142 disposed for slidable, axial movement in a casing 144 and spring biased to engage the end edge 148 a cylindrical member 146 which is attached to move with the piston.
  • the pin 142 is retracted to unlock the piston by the force of a pressurized fluid acting on the pin and introduced into casing 144 by suitable passageways 150.
  • synchronous clutch assembly 10 The operation of synchronous clutch assembly 10 will be summarized with the assumption that it is employed in a gas turbine engine propulsion system for a marine vessel which system has a planetary gear speed reducer 14 and brake assembly 16 as shown in FIG. 1.
  • the propulsion system With the synchronous clutch assembly 10 in the operative position where the piston and switch element 76 is located so that splines 82 and 88 are in mesh (as shown in FIG. 6, and when switch element 76 is in the lefthand position as viewed in FIGS. 2 and 3), the propulsion system will be assumed to be in the forward mode of operation. In this forward mode of operation, brake subassembly 40 (see FIG. 1) is engaged to prevent rotation of carrier 24 sothat rotation of shaft 28 and sun gear 18 results in rotation of ring gear 22.
  • ring gear 22 The rotation of ring gear 22 is transmitted by second input means 36 to switch element 76 ia meshing splines 84 and 88. With splines 84 and 88 in mesh, output member or shaft 42 is rotated in a direction to propel the ship for wardly.
  • a suitable command signal is produced to immediately reduce the speed of the gas turbine engine (not shown) by reducing the fuel flow to the engine.
  • signals are directed to the brake assembly 16 to release brake subassembly 40 so that both carrier 24 and ring gear 22 are free to rotate and, hence, free of the inertia of gear 18, drive shaft 28, and the engine (not shown).
  • Pressurized fluid such as oil is then introduced, via appropriate passageways 150, to retract pin 142 of locking device 140 and thereby free the piston of mechanism 44 for movement. Thereafter, pressurized fluid is conducted, through appropriate passageways from a suitable source thereof, including passageway 74, to working chamber 64 so as to exert on piston head a force toward the right as viewed in the drawings.
  • the torque load on splines 110 places a torque load on blocker splines 92 so as to keep surfaces 130 and 134 of blocker splines 92 and 110 in contact and thereby effects transmission of the axial thrust force of the piston of mechanism 44, through the blocker spline abutment, to shuttle 48.
  • the axial thrust force on shuttle 48 compresses the discs 116 of clutch pack 106 thereby accelerating first input member 34 up to the speed of switch element 76 and shuttle 48.
  • first input member 34 reaches the same speed as switch element 76 the reactive tangential force component resulting from the axial thrust force acting through the abutting inclined surfaces 130 and 134 of blocker splines 92 and 110, rotates switch element 76 until blocker splines 92 abut blocker splines 110 of shuttle 48, as is shown in FIG.
  • brake subassembly 38 is released and simultaneously pressurized fluid is conveyedto working chamber 64 of mechanism 44 to effect movement of piston head 58 to the left as viewed in the drawings.
  • switch element 76 With initial axial movement of switch element 76, splines 86 are rotatively disengaged from splines 90.
  • the shuttle 48 is maintained in rotative connection with switch means 76 through the meshing relationship of blocker splines 92 and 110.
  • blocker splines 92 tangentially move relative to blocker splines 108 as blocker splines 92 ride on inclined surfaces 136 of blocker splines 108.
  • switch element 76 brings blocker splines 92 and 108 into mesh simultaneously with carrying splines 84 into mesh with splines 88 of second input member 36.
  • brake subassembly 40 is actuated to prevent rotation of carrier 24 and thereby restoring forward mode of propulsion.
  • the present invention provides a novel synchronous clutch assembly capable of alternately connecting an output member to two concentrically arranged input members. It is relatively simple in construction since only one pressurized fluid actuated rectilinear motor means is required to effect such shifting. It is also an assembly wherein proper synchronous alignment of meshing drive splines is automatically achieved, thus eliminating the necessity for occasional recycling that conventional assemblies require.
  • a synchronous clutch assembly for alternately connecting said first and second input members to said output member, said synchronous clutch assembly comprising:
  • a switch means comprising:
  • a-l a double-acting piston-cylinder mechanism connected to rotate said output member and supported for reciprocative movement to two operative positions;
  • said mechanism having third splines disposed to alternately mesh in the two operative positions with said first and second splines on said first and second input members;
  • a shuttle means disposed and supported for rotative and linear movement adjacent said first and second input members and having two axially spaced fourth and fifth splinesf e-l. said mechanism being provided with sixth splines for alternately engaging said fourth and fifth splines of said shuttle means upon reciprocative movement of said mechanism;
  • said shuttle means being connected to said mechanism for conjoined rotation and linear movement relative to said mechanism to effect alternate engagement of said slip-clutch means of said first and second input members to thereby synchronize rotation of said output member and the input member to be connected thereto prior to said third splines meshing with the first or second splines associated with the input member to be connected.
  • a-2 fourth splines disposed to alternately engage and mesh with said fourth and fifth splines upon reciprocative linear movement of said mechanism; b-2. a plurality of preloaded detents; c-2. said shuttle means having annular inclined walls disposed to receive said detents so that an axial force is applied to said shuttle means upon reciprocative linear movement of said mechanism.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
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US409919A 1973-10-26 1973-10-26 Synchronous clutch assembly for a transmission device Expired - Lifetime US3860101A (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US409919A US3860101A (en) 1973-10-26 1973-10-26 Synchronous clutch assembly for a transmission device
NL7414014A NL7414014A (nl) 1973-10-26 1974-10-25 Synchroniseerinrichting voor koppelingeenheid van een overbrenging.

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US409919A US3860101A (en) 1973-10-26 1973-10-26 Synchronous clutch assembly for a transmission device

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Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4349090A (en) * 1979-04-20 1982-09-14 Zahnradfabrik Friedrichshafen Ag Clutch assembly for gear transmission
EP0184077A1 (de) * 1984-12-07 1986-06-11 GETRAG Getriebe- und Zahnradfabrik GmbH Synchronisiereinrichtung für Schaltkupplungen
EP0253187A1 (de) * 1986-07-04 1988-01-20 GETRAG Getriebe- und Zahnradfabrik GmbH Synchronisiereinrichtung für Schaltkupplungen
DE3728903C1 (de) * 1987-08-29 1988-11-24 Daimler Benz Ag Kupplungsverzahnung einer sperrsynchronisierten Schaltkupplung insbesondere eines Gangwechselgetriebes mit von ihrer Welle abschaltbaren Zahnraedern
EP0331362A1 (en) * 1988-02-26 1989-09-06 Arthur Knowles Drive engagement delay device
EP0390335A2 (en) * 1989-03-27 1990-10-03 General Motors Corporation Multispeed power transmission
EP0425195A1 (en) * 1989-10-25 1991-05-02 Eaton Corporation Synchronizer
EP0431295A1 (de) * 1989-12-02 1991-06-12 Benz & Hilgers GmbH Vorrichtung zum Ein- und Auskuppeln einer Antriebswelle einer Arbeitsstation einer Maschine, insbesondere einer Verpackungsmaschine
US5103952A (en) * 1990-12-24 1992-04-14 Eaton Corporation Pre-engergizer for one-way synchronizer
US5161423A (en) * 1990-12-24 1992-11-10 Eaton Corporation Self-energizing synchronizer for equalizing shift time and effort of a multi-ratio transmission
EP0843107A1 (de) * 1996-11-13 1998-05-20 Daimler-Benz Aktiengesellschaft Synchronisiereinrichtung eines Zahnräderwechselgetriebes
GB2323642A (en) * 1997-01-16 1998-09-30 Ford Global Tech Inc Synchroniser with re-indexing means comprising modified splines and lugs
WO1999023398A2 (en) * 1997-11-03 1999-05-14 Ker-Train Holdings Ltd. Planetary transmission
FR2840043A1 (fr) * 2002-05-23 2003-11-28 Antonov Automotive Europ Dispositif de transmission, pour vehicule terrestre, notamment voiturette
WO2004005738A1 (de) * 2002-07-02 2004-01-15 Zf Friedrichshafen Ag Hydraulisch betätigbare getriebeschaltung mit einer synchronisiereinrichtung
US20060163989A1 (en) * 2002-07-10 2006-07-27 Koji Kawaguchi Blue color filter, and organic electroluminescent device using the same
US20090055060A1 (en) * 2007-02-23 2009-02-26 Yamaha Hatsudoki Kabushiki Kaisha Clutch Controller, Method of Controlling Clutch, and Straddle-Type Vehicle
CN101699094B (zh) * 2009-11-12 2012-10-24 奇瑞汽车股份有限公司 一种变速器的同步装置
DE102012202496A1 (de) * 2012-02-17 2013-08-22 Zf Friedrichshafen Ag Koppeleinrichtung

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US2397943A (en) * 1942-03-02 1946-04-09 Mack Mfg Corp Synchronizing mechanism
US2410511A (en) * 1944-08-26 1946-11-05 Int Harvester Co Synchronizing device
US2930462A (en) * 1956-10-29 1960-03-29 Mack Trucks Pre-balk synchronizer
US3048247A (en) * 1957-12-12 1962-08-07 Clark Equipment Co Friction clutch with positive lock
US3369639A (en) * 1966-06-06 1968-02-20 Twin Disc Clutch Co Fluid actuated clutch with modulated exhaust valve
US3424285A (en) * 1967-04-12 1969-01-28 Allis Chalmers Mfg Co Control mechanism for shifting and braking a shiftable clutching member

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US2397943A (en) * 1942-03-02 1946-04-09 Mack Mfg Corp Synchronizing mechanism
US2389490A (en) * 1944-03-07 1945-11-20 Higgins Ind Inc Transmission device
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US2930462A (en) * 1956-10-29 1960-03-29 Mack Trucks Pre-balk synchronizer
US3048247A (en) * 1957-12-12 1962-08-07 Clark Equipment Co Friction clutch with positive lock
US3369639A (en) * 1966-06-06 1968-02-20 Twin Disc Clutch Co Fluid actuated clutch with modulated exhaust valve
US3424285A (en) * 1967-04-12 1969-01-28 Allis Chalmers Mfg Co Control mechanism for shifting and braking a shiftable clutching member

Cited By (35)

* Cited by examiner, † Cited by third party
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US4349090A (en) * 1979-04-20 1982-09-14 Zahnradfabrik Friedrichshafen Ag Clutch assembly for gear transmission
US4817773A (en) * 1984-12-07 1989-04-04 Getrag Getriebe-Und Zahnradfabrik Gmbh Synchronizing mechanism for clutches
EP0184077A1 (de) * 1984-12-07 1986-06-11 GETRAG Getriebe- und Zahnradfabrik GmbH Synchronisiereinrichtung für Schaltkupplungen
EP0253187A1 (de) * 1986-07-04 1988-01-20 GETRAG Getriebe- und Zahnradfabrik GmbH Synchronisiereinrichtung für Schaltkupplungen
US4836348A (en) * 1986-07-04 1989-06-06 Getrag Getriebe Und Zahnradfabrik Gmbh Synchronizing mechanism for shifting clutches
US4905806A (en) * 1987-08-29 1990-03-06 Daimler-Benz Ag Synchronizing shift clutch toothing arrangement
FR2619883A1 (fr) * 1987-08-29 1989-03-03 Daimler Benz Ag Denture d'accouplement d'un accouplement de transmission synchronise en blocage
DE3728903C1 (de) * 1987-08-29 1988-11-24 Daimler Benz Ag Kupplungsverzahnung einer sperrsynchronisierten Schaltkupplung insbesondere eines Gangwechselgetriebes mit von ihrer Welle abschaltbaren Zahnraedern
EP0331362A1 (en) * 1988-02-26 1989-09-06 Arthur Knowles Drive engagement delay device
US4934498A (en) * 1988-02-26 1990-06-19 Arthur Knowles Drive engagement delay device
EP0390335A2 (en) * 1989-03-27 1990-10-03 General Motors Corporation Multispeed power transmission
EP0390335A3 (en) * 1989-03-27 1991-12-11 General Motors Corporation Multispeed power transmission
EP0425195A1 (en) * 1989-10-25 1991-05-02 Eaton Corporation Synchronizer
EP0431295A1 (de) * 1989-12-02 1991-06-12 Benz & Hilgers GmbH Vorrichtung zum Ein- und Auskuppeln einer Antriebswelle einer Arbeitsstation einer Maschine, insbesondere einer Verpackungsmaschine
US5103952A (en) * 1990-12-24 1992-04-14 Eaton Corporation Pre-engergizer for one-way synchronizer
US5161423A (en) * 1990-12-24 1992-11-10 Eaton Corporation Self-energizing synchronizer for equalizing shift time and effort of a multi-ratio transmission
EP0843107A1 (de) * 1996-11-13 1998-05-20 Daimler-Benz Aktiengesellschaft Synchronisiereinrichtung eines Zahnräderwechselgetriebes
GB2323642B (en) * 1997-01-16 2001-03-14 Ford Global Tech Inc Clutch for drivably connecting relatively rotating members
GB2323642A (en) * 1997-01-16 1998-09-30 Ford Global Tech Inc Synchroniser with re-indexing means comprising modified splines and lugs
US6669594B2 (en) 1997-11-03 2003-12-30 Ker-Train Holdings Ltd. Coplanar reverted gear train loop
WO1999023398A3 (en) * 1997-11-03 1999-09-30 Ker Train Holdings Ltd Planetary transmission
US6418810B1 (en) 1997-11-03 2002-07-16 Ker-Train Holdings Ltd. Coplanar reverted gear train loop
WO1999023398A2 (en) * 1997-11-03 1999-05-14 Ker-Train Holdings Ltd. Planetary transmission
US6126566A (en) * 1997-11-03 2000-10-03 Ker-Train Holdings Ltd. Coplanar reverted gear train loop
CN100394070C (zh) * 2002-05-23 2008-06-11 安东诺夫汽车技术有限公司 用于机动车例如轻型机动车的传动装置
FR2840043A1 (fr) * 2002-05-23 2003-11-28 Antonov Automotive Europ Dispositif de transmission, pour vehicule terrestre, notamment voiturette
WO2003100292A1 (fr) * 2002-05-23 2003-12-04 Antonov Automotive Technologies B.V. Dispositif de transmission, pour vehicule terrestre, notamment voiturette
WO2004005738A1 (de) * 2002-07-02 2004-01-15 Zf Friedrichshafen Ag Hydraulisch betätigbare getriebeschaltung mit einer synchronisiereinrichtung
US7163094B2 (en) 2002-07-02 2007-01-16 Zf Friedrichshafen Ag Hydraulically actuatable gearshift system comprising a synchronizing device
US20050241903A1 (en) * 2002-07-02 2005-11-03 Wolfgang Rebholz Hydraulically actuatable gearshift system comprising a synchronizing device
US20060163989A1 (en) * 2002-07-10 2006-07-27 Koji Kawaguchi Blue color filter, and organic electroluminescent device using the same
US20090055060A1 (en) * 2007-02-23 2009-02-26 Yamaha Hatsudoki Kabushiki Kaisha Clutch Controller, Method of Controlling Clutch, and Straddle-Type Vehicle
US8396636B2 (en) * 2007-02-23 2013-03-12 Yamaha Hatsudoki Kabushiki Kaisha Clutch controller, method of controlling clutch, and straddle-type vehicle
CN101699094B (zh) * 2009-11-12 2012-10-24 奇瑞汽车股份有限公司 一种变速器的同步装置
DE102012202496A1 (de) * 2012-02-17 2013-08-22 Zf Friedrichshafen Ag Koppeleinrichtung

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